CN103597230B - Vehicle torque restricting means - Google Patents

Vehicle torque restricting means Download PDF

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Publication number
CN103597230B
CN103597230B CN201180071488.1A CN201180071488A CN103597230B CN 103597230 B CN103597230 B CN 103597230B CN 201180071488 A CN201180071488 A CN 201180071488A CN 103597230 B CN103597230 B CN 103597230B
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CN
China
Prior art keywords
friction member
cover plate
plate
torque
rubbing surface
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
CN201180071488.1A
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Chinese (zh)
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CN103597230A (en
Inventor
宫川武
高桥史
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Toyota Motor Corp
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Toyota Motor Corp
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Publication of CN103597230A publication Critical patent/CN103597230A/en
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Publication of CN103597230B publication Critical patent/CN103597230B/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/02—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
    • F16D7/024—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces
    • F16D7/025—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces with flat clutching surfaces, e.g. discs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/129—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by friction-damping means
    • F16F15/1297—Overload protection, i.e. means for limiting torque
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
    • B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/44—Series-parallel type
    • B60K6/445—Differential gearing distribution type
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

Abstract

A kind of vehicle torque means that can obtain sluggish torque with simple structure is provided, be configured to frictional force (F1) that the rubbing surface between pressing plate (80) and the first friction member (88) produces and be less than the frictional force (F2) that the rubbing surface between liner plate (76) and the first friction member (88) produces, therefore when torque (T) inputs damping device (38), first produce between pressing plate (80) and the first friction member (88) and slide, liner plate (76) and the first friction member (88) rotate integratedly.Now, the sluggish torque (T1) based on the frictional force between pressing plate (80) and the first friction member (88) is produced.So, torque-limiting mechanism (68) also plays a role as retarding mechanism, therefore, it is possible to realize the torque-limiting mechanism (68) that can obtain sluggish torque with simple structure.

Description

Vehicle torque restricting means
Technical field
The present invention relates to vehicle torque restricting means, particularly relate to the structure that can obtain the torque restricting means of sluggish torque with simple structure.
Background technique
Be known to following vehicle torque restricting means, it comprises: the cover plate that can rotate around axle center; Can with this cover plate around the relative liner plate rotated of concentric; Be inserted in the friction member between described cover plate and liner plate; And for producing the pressing member of pressing force between described cover plate and liner plate.Such as, the cogging absorption plant of patent documentation 1 is one example.
The cogging absorption plant 1 that patent documentation 1 is recorded has damping mechanism 20 and is configured in the limiting unit 30(torque restricting means of outer circumferential side of this damping mechanism 20), described damping mechanism 20 comprises: the side plate 22 that can rotate around axle center, can with this side plate 22 around the relative wheel hub 21 rotated of concentric and the damping member 24 side plate 22 and wheel hub 21 elasticity linked.In addition, in cogging absorption plant 1, between wheel hub 21 and side plate 22, be provided with the retarding mechanism (thrust component, belleville spring 23c) producing the sluggish torque of one-level, be provided with limiting unit 30 at its outer circumferential side.In addition, in the cogging absorption plant 1 that patent documentation 2 is recorded, between wheel hub 21 and the first side plate 22A and the second side plate 22B, the retarding mechanism (the first retarding mechanism and the second retarding mechanism) producing the sluggish torque of secondary is provided with.
Look-ahead technique document
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Publication 2005-127507 publication
Patent documentation 2: Japanese Unexamined Patent Publication 2007-218347 publication
Patent documentation 3: Japanese Unexamined Patent Publication 2010-230162 publication
Summary of the invention
The retarding mechanism of patent documentation 1 and the retarding mechanism of patent documentation 2 are all provided between wheel hub and side plate 22, and therefore retarding mechanism is configured in inner circumferential side.Thus the action radius (turning radius) of retarding mechanism diminishes, therefore there is the problem diminished in the producible sluggish torque of retarding mechanism.In addition, in patent documentation 1, retarding mechanism and limiting unit 30(torque restricting means) independently arrange.In addition, in patent documentation 2, even if when arranging torque restricting means, also as patent documentation 1, retarding mechanism and torque restricting means are independently arranged.These retarding mechanisms and torque restricting means comprise friction member, belleville spring etc. respectively, and in citing document 1,2, because retarding mechanism and torque restricting means are independently arranged, therefore there is structure and become very complicated problem.
The present invention makes in view of above situation, and its object is to provides a kind of vehicle torque restricting means that can obtain sluggish torque with simple structure.
In order to achieve the above object, will being intended to of the invention of technological scheme 1, (a) comprising: the cover plate that can rotate around axle center; Can with this cover plate around same axle center the relative liner plate rotated; Be inserted in the friction member between this cover plate and this liner plate; And for producing the pressing member of pressing force between this cover plate and this liner plate, wherein, b () described cover plate and described friction member are configured to mutually to slide, c () described liner plate and described friction member are configured to mutually to slide, the frictional force that d frictional force that () rubbing surface between described cover plate and described friction member produces produces than the rubbing surface between described liner plate and described friction member is little, and (e) is provided with the stop member of the slippage specified between this cover plate and this friction member between described cover plate and described friction member.
So, then be configured to frictional force that the rubbing surface between described cover plate and described friction member produces and be less than the frictional force that the rubbing surface between described liner plate and described friction member produces, therefore when to torque restricting means input torque, first produce between cover plate and friction member and slide, liner plate and friction member rotate integratedly.Now, the sluggish torque based on the frictional force between cover plate and friction member is produced.That is, the cover plate and the friction member that form torque restricting means play a role as retarding mechanism.Further, when the slippage between cover plate and friction member reaches specified value, stop member carries out action, stops the slip between cover plate and friction member.Thus, torque restricting means as based between liner plate and friction member rubbing surface produce frictional force common torque limiter and play a role.So, be also used as retarding mechanism by torque restricting means, thus can realize can simply to construct the torque restricting means producing sluggish torque.In addition, if torque restricting means is configured in outer circumferential side, then the action radius of torque restricting means becomes large, even therefore large time lag torque, also can realize.
In addition be preferably, a () described cover plate comprises a pair first cover plates and the second cover plate, b () is inserted with the first friction member as described friction member between described first cover plate and described liner plate, c () is also inserted with the second friction member as described friction member between described second cover plate and this liner plate, d () is provided with the first stop member as described stop member between described first cover plate and described first friction member, e () is also provided with the second stop member as described stop member between described second cover plate and described second friction member, f slippage that () described first stop member specifies is less than the slippage that described second stop member specifies, g frictional force that () rubbing surface between described first cover plate and described first friction member produces, and the frictional force that the rubbing surface between described second cover plate and described second friction member produces, be less than the frictional force that the rubbing surface between described liner plate and described first friction member produces, h frictional force that () rubbing surface between described liner plate and described first friction member produces is less than the frictional force that the rubbing surface between this liner plate and described second friction member produces.
So, when to torque restricting means input torque, the rubbing surface at first between the first cover plate and described first friction member and the rubbing surface between the second cover plate and described second friction member produce and slide, and now produce the first sluggish torque.Further, when the first stop member is locked, produces between liner plate and the first friction member and slide, now produce the second sluggish torque.Further, when the second stop member is locked, torque restricting means plays a role as the common torque limiter based on the frictional force produced between liner plate and the second friction member.So, the torque restricting means that can obtain the sluggish torque of secondary can be realized.
In addition be preferably, (a) vehicle torque restricting means comprises: the cover plate that can rotate around axle center, can with this cover plate around same axle center the relative liner plate rotated, be inserted in the friction member between this cover plate and this liner plate, and for producing the pressing member of pressing force between this cover plate and this liner plate, wherein, b () described cover plate and described friction member are configured to mutually to slide, c () described liner plate and described friction member are configured to mutually to slide, d () is configured to: when torque is input to described vehicle torque restricting means, rubbing surface between described cover plate and described friction member first slides than the rubbing surface between described liner plate and described friction member, e () is provided with the stop member of the slippage specified between this cover plate and this friction member between described cover plate and described friction member.
So, when to torque restricting means input torque, produce between cover plate and friction member at first and slide, liner plate and friction member rotate integratedly.Now, the sluggish torque based on the frictional force between cover plate and friction member is produced.That is, the cover plate and the friction member that form torque restricting means play a role as retarding mechanism.Further, when the slippage between cover plate and friction member reaches specified value, stop member carries out action, stops the slip between cover plate and friction member.Thus, torque restricting means as based between liner plate and friction member rubbing surface produce frictional force common torque limiter and play a role.So, be also used as retarding mechanism by torque restricting means, thus can realize can simply to construct the torque restricting means producing sluggish torque.In addition, by being configured in by torque restricting means than retarding mechanism outer circumferential side side in the past, then the action radius of torque restricting means becomes large, therefore can obtain large time lag torque.
In addition be preferably, a () described cover plate comprises a pair first cover plates and the second cover plate, b () is inserted with the first friction member as described friction member between described first cover plate and described liner plate, c () is also inserted with the second friction member as described friction member between described second cover plate and this liner plate, d () is provided with the first stop member as described stop member between described first cover plate and described first friction member, e () is also provided with the second stop member as described stop member between described second cover plate and described second friction member, f slippage that () described first stop member specifies is less than the slippage that described second stop member specifies, g () is when torque is input to described vehicle torque restricting means, rubbing surface between described first cover plate and described first friction member and the rubbing surface between described second cover plate and described second friction member slide at first, then, rubbing surface between described liner plate and described first friction member slides, finally, rubbing surface between this liner plate and described second friction member slides.So, when to torque restricting means input torque, the rubbing surface at first between the first cover plate and described first friction member and the rubbing surface between the second cover plate and described second friction member produce and slide, and now produce the first sluggish torque.Further, when the first stop member is locked, produces between liner plate and the first friction member and slide, now produce the second sluggish torque.Further, when the second stop member is locked, torque restricting means plays a role as the common torque limiter based on the frictional force produced between liner plate and the second friction member.So, the torque restricting means that can obtain the sluggish torque of secondary can be realized.
In addition be preferably, described torque restricting means, comprising: multiple described first friction member of (a) configured separate in the circumferential; B () specifies multiple described first stop member of the slippage of this first friction member multiple and described first cover plate; Multiple described second friction member of (c) configured separate in the circumferential; D () specifies multiple described second stop member of the slippage of this second friction member multiple and described second cover plate, e () described multi-disc first friction member and multi-disc second friction member have mutually different friction factor between described liner plate, have the friction member of the large rubbing surface of friction factor between described liner plate, the slippage of described first stop member or described second stop member defined is set larger.So, different by the friction factor of the rubbing surface making multiple first friction member and multiple second friction member and liner plate, thus the torque restricting means that can obtain the sluggish torque of multistage can be realized.
Accompanying drawing explanation
The summary construction diagram of the vehicle driving apparatus of Fig. 1 hybrid form of the present invention that has been application.
Fig. 2 is the sectional view of the structure for describing the damping device shown in Fig. 1 in detail.
Fig. 3 is by the amplification view of the torque-limiting mechanism partial enlargement of Fig. 2.
Fig. 4 observes the pressing plate of Fig. 3 and the direction view of the first friction member from arrow A side.
Fig. 5 is the figure representing the torque of the damping device being delivered to Fig. 2 and the relation of torsion angle.
Fig. 6 is the sectional view of the structure of the torque-limiting mechanism of damping device for illustration of another embodiment of the present invention.
Fig. 7 is the figure representing the torque of the damping device being delivered to Fig. 6 and the relation of torsion angle.
Fig. 8 is the sectional view of the torque-limiting mechanism of the damping device of another embodiment of the present invention.
Fig. 9 is the A direction view observing pressing plate the torque-limiting mechanism of Fig. 8 and the first friction member from the arrow A side of Fig. 8.
Figure 10 is the B direction view observing support plate the torque-limiting mechanism of Fig. 8 and the second friction member from the arrow B side of Fig. 8.
Figure 11 is the figure representing the torque of the damping device being delivered to Fig. 8 and the relation of torsion angle.
Figure 12 is the figure of the another way representing stop member.
Figure 13 is the figure of the another mode representing stop member.
Figure 14 is the figure of the another mode representing stop member.
Figure 15 is the figure of the relation of torque when representing the stop member employing Figure 14 and torsion angle.
Embodiment
Below, embodiments of the present invention will be described in detail with reference to the accompanying drawings.In addition, below in an example, to have carried out suitably simplifying or distortion for figure, the size of each several part when shape etc. may not be described accurately.
Embodiment 1
The summary construction diagram of the vehicle driving apparatus 10 of Fig. 1 hybrid form of the present invention that has been application.In FIG, in this vehicle driving apparatus 10, the torque of the first driving source 12 as main driving source in vehicle is passed to the wheel side output shaft 14 played a role as output link, and torque is passed to pairing left and right driving wheel 18 from this wheel side output shaft 14 via differential gearing 16.In addition, the second motor MG2 is provided with as the second driving source at this vehicle driving apparatus 10, the power that second motor MG2 optionally can perform the driving force exported for travelling runs control and the Regeneration control for recovered energy, and this second motor MG2 links via automatic transmission 22 and above-mentioned wheel side output shaft.Thus the Driving Torque transmitted from the second motor MG2 to wheel side output shaft is corresponding to the rotational speed Nout of the rotational speed Nmg2/ wheel side output shaft of the change gear s(=second motor MG2 set in this automatic transmission 22) and increase and decrease.
The automatic transmission 22 that power transfer path between the second motor MG2 and driving wheel 18 is installed, be configured to make change gear s be greater than the multiple grades of establishments of " 1 ", when running from the power of the second motor MG2 Driving Torque, with can increasing this torque to the transmission of wheel side output shaft, therefore the second motor MG2 can be configured to more low capacity or more small-sized.Thus, such as when along with the high speed of a motor vehicle, the rotational speed Nout of wheel side output shaft increases, in order to the running efficiency of the second motor MG2 is maintained kilter, reduce change gear s and to reduce the rotational speed of the second motor MG2 (following, be called the second motor rotation velocity) Nmg2, in addition, when the rotational speed Nout of wheel side output shaft reduces, increase change gear s and increase the second motor rotation velocity Nmg2.
Above-mentioned first driving source 12 is using following and formed: as the motor 24 of main power source; First motor MG1; And as synthesizing between described motor 24 and the first motor MG1 or the planetary gear system 26 of power splitting mechanism of distribution of torque.Above-mentioned motor 24 is that petrol engine, diesel engine etc. make fuel combustion carry out the known internal-combustion engine of outputting power, be configured to the electric control device (E-ECU) of the not shown engine control utilized based on microcomputer, electronically control throttle opening, suck the operating conditions such as air quantity, fuel feed, time of ignition.To the supply of above-mentioned electric control device come the operation amount of Autonomous test gas pedal throttle operation quantity sensor AS, for detect brake petal operation with presence or absence of the testing signal of brake sensor BS etc.
Above-mentioned first motor MG1 is such as synchronous motor, is configured to optionally produce as the generation function of motor of driving torque and the function as generator, is connected with the electric accumulator such as battery, capacitor 32 via transducer (inverter) 30.Further, control this transducer 30 by the electric control device (MG-ECU) controlled by the not shown motor generator set based on microcomputer, thus regulate or set Driving Torque or the regenerative torque of the first motor MG1.
Planetary gear system 26 is the planetary gears having following three rotary element and produce single small gear (singlepinion) type of known differential action: sun gear S0; Relative to this sun gear S0 in the gear ring R0 configured circularly with one heart; Can free rotation and the planetary wheel carrier CA0 supported with freely revolving round the sun to the small gear P0 engaged with these sun gears S0 and gear ring R0.Planetary gear system 26 is arranged with one heart with motor 24 and automatic transmission 22.Because planetary gear system 26 and automatic transmission 22 are configured to symmetrical relative to center line, therefore omit lower half portion of these parts in FIG.
In the present embodiment, the crankshaft 36 of motor 24 links with the planetary wheel carrier CA0 of planetary gear system 26 via damping device 38 and power transmission shaft 39.And the first motor MG1 is linked to sun gear S0, wheel side output shaft is linked to gear ring R0.This planetary wheel carrier CA0 plays a role as input key element, and sun gear S0 plays a role as counter-force key element, and gear ring R0 plays a role as output key element.
In above-mentioned planetary gear system 26, if for the Driving Torque of motor 24 being input to planetary wheel carrier CA0, the counter-force torque produced by the first motor MG1 is input to sun gear S0, then occur direct transmitting torque at the gear ring R0 becoming output key element, therefore the first motor MG1 plays a role as generator.In addition, the rotational speed of gear ring R0 and rotational speed (output shaft rotational speed) Nout of wheel side output shaft 14 constant time, by making the rotational speed Nmg1 of the first motor MG1 change up and down, thus the rotational speed of motor 24 (engine rotary speed) Ne (stepless) change continuously can be made.
The described automatic transmission 22 of the present embodiment is made up of one group of La Weina (ravigneaux) formula planetary gears.Namely, the first sun gear S1 and secondary sun wheel S2 is provided with in automatic transmission 22, the large-diameter portion of stepped pinion (steppedpinion) P1 engages with this first sun gear S1, and the minor diameter part of this stepped pinion P1 engages with small gear P2, this small gear P2 and the gear ring R1(R2 with described each sun gear S1, S2 concentric arrangement) engage.Above-mentioned each small gear P1, P2 are by common planetary wheel carrier CA1(CA2) respectively can free rotation and the mode freely revolved round the sun keep.In addition, secondary sun wheel S2 engages with small gear P2.
Described second motor MG2 by being controlled by transducer 40 by the electric control device (MG-ECU) that described motor generator set controls, thus plays a role as motor or generator, reconciles or sets auxiliary Driving Torque or regenerative torque.This second motor MG2 and secondary sun wheel S2 links, and above-mentioned planetary wheel carrier CA1 and wheel side output shaft link.First sun gear S1 forms the mechanism being equivalent to double-pinion type planetary gear system with gear ring R1 together with each small gear P1, P2, in addition, secondary sun wheel S2 forms with gear ring R1 the mechanism being equivalent to single pinion type planetary gear device together with small gear P2.
And, the first break B1 and second brake B2 is provided with in automatic transmission 22, described first break B1 is located between this first sun gear S1 and the housing 42 as non-rotating component to selectively fix the first sun gear S1, and second brake B2 is located between this gear ring R1 and housing 42 in order to selectively fixed gear ring R1.These breaks B1, B2 are the so-called friction engagement devices utilizing frictional force to produce braking force, can adopt the bonding apparatus of many plates form or the bonding apparatus of band forms.Further, these breaks B1, B2 is configured to correspondingly make its torque capacity consecutive variations with the activating pressure produced by the break B1 hydraulic actuators such as oil hydraulic cylinder, break B2 hydraulic actuator respectively.
The automatic transmission 22 formed as described so is configured to: secondary sun wheel S2 plays a role as input key element, planetary wheel carrier CA1 plays a role as output key element, if the first break B1 engages, the high speed level H being greater than the change gear sh of " 1 " sets up, if replace the first break B1 and second brake B2 engages, then the slow speed turbine stage L of larger than the change gear sh of this high speed level H change gear sl sets up.That is, automatic transmission 22 is 2 grades of speed changers, the speed change between described speed change level H and L based on vehicle velocity V, require the travelling states such as driving force (or throttle operation amount) and perform.More specifically, speed change level region is redefined for mapping (speed change line chart), controls in the mode setting certain speed change level according to the operating condition detected.
Fig. 2 is the sectional view of the structure for describing the damping device 38 shown in Fig. 1 in detail.In addition, half part of axle center below the C of the damping device 38 of Fig. 2 is omitted.Damping device 38 to be configured to centered by the C of axle center can between motor 24 and planetary gear system 26 transferring power.In addition, power transmission shaft 39 spline shown in Fig. 1 is embedded in the inner peripheral portion of damping device 38.
Damping device 38 comprises: the pairing left and right disc plate 56 that can rotate around axle center C; Chimeric and can not link with power transmission shaft 39 with the relative rotation by spline, and be arranged to can with disc plate 56 around the relative hub member 58 rotated of coaxial heart; With being located at resiliently deformable between disc plate 56 and hub member 58, corresponding to the amount of relative rotation between disc plate 56 and hub member 58 by disc plate 56 and hub member 58 action ground (flexibly) helical spring 62(torsion spring be made up of spring steel of linking); The retarding mechanism 64 of frictional force is produced between disc plate 56 and hub member 58; Be located at the described torque-limiting mechanism 68 of the outer circumferential side of disc plate 56.In addition, torque-limiting mechanism 68 is corresponding with vehicle torque restricting means of the present invention.
Disc plate 56 is made up of discoid first plate 70 of pairing left and right and the second plate 72, under the state sandwiching helical spring 62 vertically with these plates 70,72, is fixed makes relatively to rotate by rivet 66.In addition, rivet 66 also plays a role as the clamp structure of the liner plate 76 of torque-limiting mechanism 68 described later.Multiple the first open pore 70a for accommodating helical spring 62 is circumferentially formed at the first plate 70.In addition, also multiple the second open pore 72a for accommodating helical spring 62 is circumferentially formed with in the position corresponding with the first open pore 70a at the second plate 72.Further, multiple helical spring 62 is accommodated in the space formed by the first open pore 70a and the second open pore 72a.Thus, when disc plate 56 rotates around axle center C, helical spring 62 revolves round the sun around axle center C similarly.
Hub member 58 is formed by cylindrical part 58a and discoideus lip part 58b, and this cylindrical part 58a has for the chimeric inner circumferential tooth of power transmission shaft 39 spline in inner peripheral portion, and this lip part 58b extends from the outer circumferential face of above-mentioned cylindrical part 58a to radial outside.Further, in a rotational direction, the collecting of the space between each lip part 58b helical spring 62 is being formed at.Thus, when hub member 58 rotates around axle center C, one end of helical spring 62 abuts with hub member 58, and therefore helical spring 62 revolves round the sun around axle center C similarly.By such formation, thus helical spring 62 corresponding to the amount of relative rotation between disc plate 56 and hub member 58 resiliently deformable while disc plate 56 and hub member 58 action are linked.Such as, if disc plate 56 rotates, then one end of helical spring 62 is pressed, and the lip part 58b of the other end pressing hub member 58 of helical spring 62, makes hub member 58 rotate thus.Now, helical spring 62 resiliently deformable is while transmit rotation, thus the impact caused due to cogging is absorbed by the resiliently deformable of helical spring 62.
Retarding mechanism 64 in the inner circumferential side of helical spring 62, between the lip part 58b being located at disc plate 56 and hub member 58 in the axial direction.Further, retarding mechanism 64 is made up of multiple friction member and/or belleville spring etc., between disc plate 56 and hub member 58, produce frictional force.By adjusting this frictional force, set best sluggish torque thus.In addition, the retarding mechanism 64 of the present embodiment comprises the frictional engagement key element be made up of the friction member of low coefficient of friction and the frictional engagement key element be made up of the friction member of high coefficient of friction, produces 2 grades of sluggish torques.
Torque-limiting mechanism 68(torque restricting means of the present invention) be located at the more outer circumferential side of disc plate 56, there is the effect preventing the transmission of torque exceeding the torque-limiting Tlim preset.Torque-limiting mechanism 68 comprises: fastening by rivet 66 together with disc plate 56, thus the liner plate 76 of the annulus tabular rotated around axle center C integratedly with disc plate 56; The support plate 78 be made up of the discoid first support plate 78a and the second discoideus support plate 78b that are positioned at outer circumferential side; With the discoideus pressing plate 80 of the mode being contained in support plate 78 configuration adjacent with liner plate 76; The belleville spring 82 of the taper in the gap being inserted in axially between pressing plate 80 and the first support plate 78a with preload conditions; Be inserted in the first friction member 88(friction member between pressing plate 80 and liner plate 76); Be inserted in the second friction member 89 between the inner peripheral portion of the second support plate 78b and liner plate 76.In addition, pressing plate 80 is corresponding with cover plate of the present invention.
Fig. 3 is by the amplification view of torque-limiting mechanism 68 partial enlargement of Fig. 2.Below, be described with reference to Fig. 3.Support plate 78 is made up of the discoid first support plate 78a of pairing left and right and the second discoideus support plate 78b, is formed with the bolt hole 84,86 of the not shown bolton for the flywheel 50 of Fig. 1 and support plate 78a, 78b being fixed at its peripheral part respectively.
First support plate 78a, its inner peripheral portion bends vertically, is formed with space thus between the first support plate 78a and the second support plate 78b.In this space, contain belleville spring 82, pressing plate 80, first friction member 88, liner plate 76 and the second friction member 89 from the first support plate 78a vertically successively towards the second support plate 78b ground.
Liner plate 76 is the components of the annulus tabular of being fixed by rivet 66 together with the first plate 70 and the second plate 72.In addition, pressing plate 80 is formed as annulus tabular too.This pressing plate 80 and liner plate 76 are configured to relatively to rotate around identical axle center C.In addition, between this pressing plate 80 and liner plate 76, the first friction member 88 is inserted with.First friction member 88 is such as formed as annulus tabular.Or the first friction member 88 can be formed as arc-shaped, and circumferentially equal angles compartment of terrain is arranged.
At this, in the first friction member 88, the rubbing surface of side adjacent with pressing plate 80 is configured to slide with this pressing plate 80.In addition, at the rubbing surface adjacent with liner plate 76 of the first friction member 88, be also configured to slide with this liner plate 76.That is, the first friction member 88 is not all fixed relative to adjacent pressing plate 80 and liner plate 76.
In addition, the coefficientoffrictionμ 1 of the rubbing surface (slip surface) between pressing plate 80 and the first friction member 88 is less than the coefficientoffrictionμ 2 of the rubbing surface (slip surface) between liner plate 76 and the first friction member 88.That is, the frictional force F1 that the rubbing surface between pressing plate 80 and the first friction member 88 produces is less than the frictional force F2 that the rubbing surface between liner plate 76 and the first friction member 88 produces.
In addition, between pressing plate 80 and the first friction member 88, the stop member 90 of the CLV ceiling limit value for specifying the slippage (amount of relative rotation) between this pressing plate 80 and first friction member 88 is provided with.Stop member 90 by from pressing plate 80 with the rubbing surface that the first friction member 88 rubs to axially outstanding columned raised 92 and the backstop hole 94 of the round shape that is formed at the first friction member 88 form.Projection 92 is contained in backstop hole 94, forms the space (gap) of the circumference (sense of rotation) for specifying predetermined slippage between pressing plate 80 with the first friction member 88 (relative rotate).
Fig. 4 is the direction view observing pressing plate 80 Fig. 3 and the first friction member 88 from arrow A side.As shown in Figure 3, backstop hole 94 is formed as the hole of the round type larger than the diameter of projection 92.Thus, between projection 92 and backstop hole 94, form space, with the amount in this space correspondingly, allow the slip to sense of rotation between pressing plate 80 and the first friction member 88.Thus if the slippage between pressing plate 80 and the first friction member 88 becomes specified value, then projection 92 abuts with the wall in backstop hole 94, and pressing plate 80 can not rotate relatively with the first friction member 88.
In addition, between the inner peripheral portion and liner plate 76 of the second support plate 78b, the second friction member 89 is inserted with.Second friction member is formed as such as annulus tabular in the same manner as the first friction member 88.Or the second friction member 89 can be formed as arc-shaped, and circumferentially equal angles compartment of terrain is arranged.
In second friction member 89, the rubbing surface of itself and the second adjacent side of support plate 78b is configured to slide with this second support plate 78b, is also configured to slide with this liner plate 76 at the rubbing surface adjacent with liner plate 76.That is, the second friction member 89 is not all fixed relative to the second adjacent support plate 78b and liner plate 76.In addition, the coefficientoffrictionμ of the rubbing surface (slip surface) between the second support plate 78b and the second friction member 89 and the rubbing surface (slip surface) between liner plate 76 and the second friction member 89 is all set as coefficientoffrictionμ 2.
Belleville spring 82 is inserted between the first support plate 78a and pressing plate 80 with preload conditions.Belleville spring 82 is formed as taper, and its inner peripheral end thereof abuts with pressing plate 80, and peripheral end abuts with the first support plate 78a, is inserted into being deformed into described in generation the deflection preloading (belleville spring load W).Thus belleville spring 82 presses pressing plate 80 towards liner plate 76 side vertically with belleville spring load W.Thus, between pressing plate 80 and the first friction member 88, between liner plate 76 and the first friction member 88, between the second support plate 78b and the second friction member 89 and between liner plate 76 and the second friction member 89, frictional force F is produced.In addition, belleville spring 82 is corresponding with pressing member of the present invention.
The action of the damping device 38 formed as described above is described.Fig. 5 represents the relation being input to the torque T of damping device 38 and the torsion angle of damping device 38.In addition, transverse axis represents torsion angle, and the longitudinal axis represents torque T.If torque T is input to damping device 38, torsion angle increases and reaches torsion angle 1, then first, the rubbing surface between the low pressing plate 80 of coefficientoffrictionμ 1 and the first friction member 88 produces and slides, and now, produces sluggish torque T1.In addition, sluggish torque T1 is now by shown in following formula (1).At this, r1 represents the action radius (turning radius) of the first friction member 88, and W represents the belleville spring load of belleville spring 82.
T1＝r1×μ1×Ｗ···（1）
Further, when torsion angle reaches θ 2, the slippage that stop member 90 allows reaches specified value.Now, at stop member 90, projection 92 abuts with backstop hole 94, and pressing plate 80 becomes can not relatively rotate with the first friction member 88.That is, the slip between pressing plate 80 and the first friction member 88 is limited.Then, the rubbing surface between liner plate 76 and the first friction member 88 produces and slides.The torque T2 now produced is following formula (2).At this, coefficientoffrictionμ 2 is greater than coefficientoffrictionμ 1, and therefore torque T2 is greater than torque T1(T2 > T1).This torque T2 becomes the torque-limiting Tlm of torque-limiting mechanism 68.
T2＝r1×μ2×Ｗ···（2）
Thus, at torque-limiting mechanism 68, achieve the sluggish torque T1 of one-level.At this, torque-limiting mechanism 68 is configured in than disc plate 56 outer circumferential side side, and therefore action radius (turning radius) r1 of the first friction member 88 becomes large.Thus, by adjusting the belleville spring load W of coefficientoffrictionμ 1 and belleville spring 82, the sluggish torque from little sluggish torque to the such wide range of large time lag torque can be obtained, so the degrees of freedom of design significantly improves.In addition, because torque-limiting mechanism 68 also plays a role as retarding mechanism, namely torque-limiting mechanism 68 is also used as retarding mechanism, therefore can produce the torque-limiting mechanism 68 of sluggish torque with simple constitution realization.
In addition, because retarding mechanism is in the past located at the inner peripheral portion of damping device, be therefore difficult to obtain large time lag torque.In order to obtain large time lag torque in retarding mechanism in the past, need to use high coefficient of friction material, and increase the pressing load of belleville spring, but the wearability of high coefficient of friction material is poor, if the pressing load of belleville spring increases, the counter-force that then circumferential component is born becomes large, therefore needs the intensity improving these parts.Thus, be difficult to obtain large time lag torque.
On the other hand, in the present embodiment, owing to being provided with sluggish torque mechanism at torque-limiting mechanism 68, therefore the action radius (turning radius) of friction member becomes large, even large time lag torque, also can easily realize.Such as, in the past, be difficult to utilize sluggish torque to make resonance or the engine motoring torque decay of the input more than as the peak torque of motor.On the other hand, in the present embodiment, the sluggish torque of the peak torque being greater than motor can be produced, therefore, it is possible to resonate time or engine start time utilize sluggish torque to decay.
As mentioned above, according to the present embodiment, be configured to frictional force F1 that the rubbing surface between pressing plate 80 and the first friction member 88 produces and be less than the frictional force F2 that the rubbing surface between liner plate 76 and the first friction member 88 produces, therefore when torque T is input to damping device 38, first produce between pressing plate 80 and the first friction member 88 and slide, liner plate 76 and the first friction member 88 rotate integratedly.Now, the sluggish torque T1 based on the frictional force between pressing plate 80 and the first friction member 88 is produced.That is, the pressing plate 80 and the first friction member 88 that form torque-limiting mechanism 68 play a role as retarding mechanism.Further, when the slippage between pressing plate 80 and the first friction member 88 reaches specified value, stop member 90 action, stops the slip between pressing plate 80 and the first friction member 88.Thus, the common torque that torque-limiting mechanism 68 carries out the frictional force produced based on the rubbing surface between liner plate 76 and the first friction member 88 limits.So, torque-limiting mechanism 68 is also used as retarding mechanism, thus can produce the torque-limiting mechanism 68 of sluggish torque with simple constitution realization.In addition, this torque-limiting mechanism 68 is configured in than disc plate 56 outer circumferential side side, and therefore the action radius (turning radius) of torque-limiting mechanism 68 becomes large, even therefore large time lag torque, also can realize.In addition, by using low-friction material etc., even thus little sluggish torque, also can easily obtain.And then this structure can not need increase number of components and easily form.
In addition, according to the present embodiment, this structure compared with structure in the past, just make the friction factor on the two sides of friction member variant, form backstop hole 94 at friction member and form projection 92 at pressing plate 80, therefore without the need to implementing large design alteration, the sluggish torque of wide range can just be produced.
In addition, in the present embodiment, there is secondary retarding mechanism 64, therefore add the sluggishness of torque-limiting mechanism 68, three grades of sluggish torques can be realized.
Then, other embodiments of the present invention are described.In addition, in the following description, identical reference character marked for the part common with the above embodiments and omit the description.
Embodiment 2
Fig. 6 is the sectional view of the structure of the torque-limiting mechanism 102 had for illustration of the damping device 100 of other embodiments of the present invention, corresponding with the Fig. 3 in above-described embodiment.Support plate 104 is made up of the discoid first support plate 104a of pairing left and right and the second discoideus support plate 104b.First support plate 104a, its inner peripheral portion bends vertically, is formed with space thus between the first support plate 104a and the second support plate 104b.In this space, contain belleville spring 108, pressing plate 106, first friction member 110, liner plate 76 and the second friction member 112 from the first support plate 104a towards the second support plate 104b.In addition, torque-limiting mechanism 102 is corresponding with vehicle torque restricting means of the present invention, first friction member 110 is corresponding with the first friction member of the present invention, second friction member 112 is corresponding with the second friction member of the present invention, pressing plate 106 is corresponding with the first cover plate of the present invention, second support plate 104b is corresponding with the second cover plate of the present invention, and belleville spring 108 is corresponding with pressing member of the present invention.
Pressing plate 106 and the second support plate 104b are configured to rotate around axle center C, and liner plate 76 can rotate around axle center C relatively relative to these pressing plates 106 and the second support plate 104b.
The first friction member 110 is inserted with between pressing plate 106 and liner plate 76.First friction member 110 is configured to slide with this pressing plate 106 at the rubbing surface of side adjacent with pressing plate 106, at the rubbing surface adjacent with liner plate 76, is configured to slide with this liner plate 76.That is, the first friction member 110 is not all fixed relative to pressing plate 106 and liner plate 76.
In addition, the coefficientoffrictionμ 1 of the rubbing surface (slip surface) between pressing plate 106 and the first friction member 110 is less than the coefficientoffrictionμ 2 of the rubbing surface (slip surface) between liner plate 76 and the first friction member 110.That is, the frictional force F1 produced between pressing plate 106 and the first friction member 110 is less than the frictional force F2 produced between liner plate 76 and the first friction member 110.
In addition, between pressing plate 106 and the first friction member 110, the first stop member 116(first stop member of the CLV ceiling limit value for specifying the slippage (amount of relative rotation) between this pressing plate 106 and first friction member 110 is provided with).First stop member 116 is made up of the backstop hole 120 of the outstanding vertically columned projection 118 of the rubbing surface rubbed with the first friction member 110 from pressing plate 106 and the round type that is formed at the first friction member 110.Projection 118 is contained in backstop hole 120, forms the L1(gap, space of the circumference (sense of rotation) for specifying slippage between pressing plate 106 with the first friction member 110 (relative rotate)).
In addition, between the inner peripheral portion and liner plate 76 of the second support plate 104b, the second friction member 112 is formed with.Second friction member 112, the rubbing surface of itself and the second adjacent side of support plate 104b is configured to slide with this second support plate 104b, is also configured to slide with this liner plate 76 at the rubbing surface adjacent with liner plate 76.That is, the second friction member 112 is not all fixed relative to the second support plate 104b and liner plate 76.
In addition, the rubbing surface (slip surface) between the second support plate 104b and the second friction member 112 is set as coefficientoffrictionμ 1.That is, equal with the coefficientoffrictionμ 1 of the rubbing surface (slip surface) between pressing plate 106 and the first friction member 110.In addition, the coefficientoffrictionμ 3 of the rubbing surface (slip surface) between liner plate 76 and the second friction member 112 is greater than the coefficientoffrictionμ 2 of the rubbing surface (slip surface) between liner plate 76 and the first friction member 110.
Thus, the coefficientoffrictionμ 1 of the coefficientoffrictionμ 1 of the rubbing surface (slip surface) between pressing plate 106 and the first friction member 110 and the rubbing surface (slip surface) between the second support plate 104b and the second friction member 112 is minimum, the coefficientoffrictionμ 2 of the rubbing surface (slip surface) between liner plate 76 and the first friction member 110 is greater than coefficientoffrictionμ 1, and the coefficientoffrictionμ 3 of the rubbing surface (slip surface) between liner plate 76 and the second friction member 112 is maximum (μ 3 > μ 2 > μ 1).Thus the frictional force F1 produced between pressing plate 106 with the first friction member 110 and frictional force F1 produced between the second support plate 104b with the second friction member 112 is equal, and is less than the frictional force F2 produced between liner plate 76 and the first friction member 110.In addition, the frictional force F2 produced between liner plate 76 and the first friction member 110 is less than the frictional force F3(F3 > F2 > F1 produced between liner plate 76 and the second friction member 112).
In addition, between the second support plate 104b and the second friction member 112, the second stop member 122(second stop member for specifying the slippage (amount of relative rotation) between this second support plate 104b and the second friction member 112 is provided with).Second stop member 122 is made up of the backstop hole 126 of the outstanding vertically columned projection 124 of the rubbing surface rubbed with the second friction member 112 from the second support plate 104b and the round type that is formed at the second friction member 112.Projection 124 is contained in backstop hole 126, is formed with the L2(gap, space of the circumferential direction for specifying slippage between the second support plate 104b with the second friction member 112 (relative rotate)).At this, the space L2 of the second stop member 122 is configured to be greater than the space L1 set at the first stop member 116.Such as, as shown in Figure 6, projection 118,124 is formed as cylindric, and backstop hole 120,126 is formed as circular, and the diameter of projection 124 is less than the diameter of projection 118, and backstop hole 126 is formed be greater than backstop hole 120.If form like this, then the slippage of the first stop member 116 defined is less than the slippage of the second stop member 122 defined.
The action of the damping device 100 formed as described so is described.Fig. 7 represents and is delivered to the torque T of damping device 100 and the relation of torsion angle.When torque T is input to damping device 100, when torsion angle increases and reaches torsion angle 1, the rubbing surface between pressing plate 106 and the first friction member 110 and the rubbing surface between the second support plate 104b and the second friction member 112 produce slip at first.This is because the coefficientoffrictionμ 1 between pressing plate 106 and the first friction member 110 and between the second support plate 104b and the second friction member 112 is minimum.Now, the sluggish torque T1 shown in following formula (3) is produced.In formula (3), r1 represents the action radius (turning radius) of the first friction member 110, and W represents the belleville spring load of belleville spring 108.
T1＝r1×μ1×Ｗ···（3）
Further, when torsion angle reaches torsion angle 2, at the first stop member 116, projection 118 abuts with backstop hole 120, and pressing plate 106 becomes can not relatively rotate with the first friction member 110.Then, the rubbing surface between liner plate 76 and the first friction member 110 produces and slides.In addition, the rubbing surface between the second support plate 104b and the second friction member 112, slides and continues.Now, the sluggish torque T2 shown in following formula (4) is produced.In addition, μ 2 is friction factor of the rubbing surface between liner plate 76 and the first friction member 110.At this, coefficientoffrictionμ 2 is greater than coefficientoffrictionμ 1, and therefore sluggish torque T2 is greater than sluggish torque T1.
T2＝r1×μ2×Ｗ···（4）
When torsion angle increases further and reaches torsion angle 3, at the second stop member 122, projection 124 abuts with backstop hole 126, and the second support plate 104b becomes can not relatively rotate with the second friction member 112.That is, the slip between the second support plate 104b and the second friction member 112 is restricted.Further, finally, produce between liner plate 76 and the second friction member 112 and slide.Torque T3 is now by shown in following formula (5).At this, μ 3 represents the friction factor of the rubbing surface between liner plate 76 and the second friction member 112.Based on formula (5), coefficientoffrictionμ 3 is maximum, and therefore torque T3 becomes maximum.This torque T3 becomes the torque-limiting Tlm of torque-limiting mechanism 102.
T3＝r1×μ3×Ｗ···（5）
So, at torque-limiting mechanism 102, realize secondary sluggish torque T1, T2.That is, because torque-limiting mechanism 102 is also used as retarding mechanism, therefore just the torque-limiting mechanism 102 that can produce sluggish torque can be realized by simple structure.In addition, because torque-limiting mechanism 102 is configured in the outer circumferential side of disc plate 56, therefore radius (effective diameter) r1 of the first friction member 110 and the second friction member 112 is large.Thus by the belleville spring load of adjustment coefficientoffrictionμ 1 ~ μ 3, belleville spring 108, can obtain the sluggish torque of the wide range from little sluggish torque to large time lag torque, therefore design freedom significantly improves.In addition, if add the retarding mechanism 64 of the sluggish torque of generation secondary in the past, then 4 grades of sluggish torques can be realized.
As mentioned above, according to the present embodiment, if torque T is input to damping device 100, then the rubbing surface at first between pressing plate 106 and the first friction member 110 and the rubbing surface between the second support plate 104b and the second friction member 112 produce and slide, and now produce the first sluggish torque T1.Further, if the first stop member 116 is locked, then produces between liner plate 76 and the first friction member 110 and slide, now produce the second sluggish torque T2.Further, if the second stop member 122 is locked, then torque-limiting mechanism 102 carries out limiting based on the common torque of the frictional force produced between liner plate 76 and the second friction member 112.So, the torque-limiting mechanism 102 that can obtain the sluggish torque of secondary can be realized.
Embodiment 3
Fig. 8 is the torque-limiting mechanism 152(torque restricting means of the damping device 150 as another embodiment of the present invention) sectional view.In addition, the torque-limiting mechanism 152 of the present embodiment is not that embodiment described above is arranged continuously in whole circumference like that, but equiangularly arranges multiple (being 4 places in the present embodiment) at interval in circumference.As shown in Figure 8, torque-limiting mechanism 152 comprises: liner plate 76, pressing plate 156, insert the first friction member 158 between liner plate 76 and pressing plate 156, support plate 160, insert the second friction member 162 between liner plate 76 and support plate 160; And the cramping component 164 of pressing plate 156 and support plate 160 is clamped from axial two ends.In addition, torque-limiting mechanism 152 is corresponding with vehicle torque restricting means of the present invention, pressing plate 156 is corresponding with the first cover plate of the present invention, support plate 160 is corresponding with the second cover plate of the present invention, clamp component 164 corresponding with pressing member of the present invention, first friction member 158 is corresponding with the first friction member of the present invention, and the second friction member 162 is corresponding with the second friction member of the present invention.
Support plate 160 is formed as annulus tabular, and is formed with the bolt hole 166 of not shown bolton and the penetration hole 168 for making cramping component 164 run through vertically.In addition, support plate 160 and pressing plate 156 are configured to rotate around axle center C, and liner plate 76 is configured to relatively to rotate relative to described support plate 160 and pressing plate 156 around axle center C.
First friction member 158 is configured to can mutually slide (can relatively rotate) with the rubbing surface between pressing plate 156, the rubbing surface between the first friction member 158 and liner plate 76, is also configured to can mutually slide (can relatively rotate).In addition, the second friction member 162 is configured to can mutually slide (can relatively rotate) with the rubbing surface between support plate 160, and the second friction member 162 is configured to can mutually slide (can relatively rotate) with the rubbing surface between liner plate 76.
Clamp component 164(pressing member) be made up of spring steel, comprising: the first abutting part 170 that inner peripheral end thereof abuts with pressing plate 156, the second abutting part 172 abutted with support plate 160 and vertically by linking department 174 that the peripheral end of the first abutting part 170 and the second abutting part 172 links.Further, clamping component 164 utilizes preload (the belleville spring load W) preset to clamp (pressing) pressing plate 156 and support plate 160 vertically.
In addition, between pressing plate 156 and the first friction member 158, the first stop member 176(first stop member for specifying the slippage (amount of relative rotation) between (make and limit) this pressing plate 156 and first friction member 158 is provided with).First stop member 176 is made up of the outstanding vertically columned projection 178 of the rubbing surface rubbed with the first friction member 158 from pressing plate 156 and the backstop hole 180 that is formed at the first friction member 158.Projection 178 is contained in backstop hole 180, is formed with the space L1 of the sense of rotation for allowing the predetermined slippage between pressing plate 156 with the first friction member 158 (relative rotate).
In addition, between support plate 160 and the second friction member 162, the second stop member 182(second stop member for specifying the slippage (amount of relative rotation) between this support plate 160 and second friction member 162 is provided with).The projection 184 that second stop member 182 is given prominence to vertically by the rubbing surface rubbed with the second friction member 162 from support plate 160 and the backstop hole 186 being formed at the second friction member 162 are formed.In addition, the shape (external diameter) of projection 178 and projection 184 is equal.Projection 184 is contained in backstop hole 186, is formed with space (gap) L2 for the slippage (amount of relative rotation) between regulation support plate 160 and the second friction member 162.At this, space L2 is formed be greater than the space L1 of the first stop member 176.
Fig. 9 represents to observe the pressing plate 156 of the torque-limiting mechanism 152 of Fig. 8 and the A direction view of the first friction member 158 from the arrow A side of Fig. 8.In addition, Fig. 9 is simple diagram, the non-precise record such as scale.
As shown in Figure 9, at discoideus pressing plate 156, be configured with 4 the first friction members 158 with being circumferentially equiangularly spaced apart.In addition, in fig .9, first this reference character of friction member 158a is marked to the first friction member 158 being positioned at top side, from this first friction member 158a, clockwise the first friction member 158 is marked respectively the reference character of the first friction member 158b ~ the first friction member d.In addition, as shown in Figure 9, to each first friction member 158a ~ 158d, first stop member 176a ~ 176d for specifying the slippage between pressing plate 156 and the first friction member 158 is set respectively.In addition, for backstop hole 180, also mark reference character (180a ~ 180d) in the same manner as the first friction member 158.In addition, at the present embodiment, the belleville spring load W that each cramping component 164 produces is unchanged respectively.
At each first stop member 176(176a ~ 176d) in, the shape of projection 178 is identical, but each backstop hole 180(180a ~ 180d) circumferential width different.Specifically, as shown in Figure 9, be formed as in each backstop hole 180: the groove width Ha-1 of backstop hole 180a is minimum, the groove width Hb-1 of backstop hole 180b is greater than the groove width Ha-1 of backstop hole 180a, the groove width Hc-1 of backstop hole 180c is greater than the groove width Hb-1 of backstop hole 180b, and the groove width Hd-1 of backstop hole 180d is greater than the groove width Hc-1 of backstop hole 180c.
Figure 10 observes the support plate 160 of the torque-limiting mechanism 152 of Fig. 8 and the B direction view of the second friction member 162 from the arrow B side of Fig. 8.In addition, Figure 10 is simple diagram, and the non-precise record such as scale, eliminates the peripheral part of support plate 160.
As shown in Figure 10,4 the second friction members 162 are configured with being circumferentially equiangularly spaced apart at discoideus support plate 160.In addition, in Fig. 10, second this reference character of friction member 162a is marked to the second friction member 162 being positioned at top side, from this second friction member 162a, clockwise the second friction member 162 is marked respectively to the reference character of the second friction member 162b ~ the second friction member 162d.In addition, as shown in Figure 10, to each second friction member 162a ~ 162d, second stop member 182a ~ 182d of the slippage for specifying support plate 160 and the second friction member 162 is set respectively.In addition, for the backstop hole 186 of formation second stop member 182, also mark reference character (186a ~ 186d) in the same manner as the second friction member 162.
The projection 184 of second stop member 182a ~ 182d is identical with the shape of the projection 178 of the first stop member 176.On the other hand, the circumferential width of each backstop hole 186a ~ 186d is different.Specifically, as shown in Figure 10, be formed as in each backstop hole 186: the groove width Ha-2 of backstop hole 186a is minimum, the groove width Hb-2 of backstop hole 186b is greater than the groove width Ha-2 of backstop hole 186a, the groove width Hc-2 of backstop hole 186c is greater than the groove width Hb-2 of backstop hole 186b, and the groove width Hd-2 of backstop hole 186d is greater than the groove width Hc-2 of backstop hole 186c.
At this, if add, each groove width (Ha-1 ~ Hd-1) in the backstop hole 180 of the first stop member 176 carrys out more each groove width (Ha-1 ~ Hd-1, Ha-2 ~ Hd-2), be then set as meeting the relation shown in following formula (6).In addition, because the projection 178 of the first stop member 176 is identical with the shape of the projection 184 of the second stop member 182, therefore formula (6) is corresponding with the size of space L, the i.e. size of the slippage (amount of relative rotation) of each stop member 176,182 defined (permission).
Hd-2＞Hd-1＞Hc-2＞Hc-1＞Hb-2＞Hb-1＞Ha-2＞Ha-1···（6）
In addition, the coefficientoffrictionμ of the rubbing surface between pressing plate 156 and the first friction member 158a is set to μ 1, the friction factor of the rubbing surface between liner plate 76 and the first friction member 158a is set to μ 2, the coefficientoffrictionμ of the rubbing surface between support plate 160 and the second friction member 162a is set to μ 1, and the coefficientoffrictionμ of the rubbing surface between liner plate 76 and the second friction member 162a is set to μ 3.In addition, the coefficientoffrictionμ of the rubbing surface between pressing plate 156 and the first friction member 158b is set to μ 1, the coefficientoffrictionμ of the rubbing surface between liner plate 76 and the first friction member 158b is set to μ 4, the coefficientoffrictionμ of the rubbing surface between support plate 160 and the second friction member 162b is set to μ 1, and the coefficientoffrictionμ of the rubbing surface between liner plate 76 and the second friction member 162b is set to μ 5.In addition, the coefficientoffrictionμ of the rubbing surface between pressing plate 156 and the first friction member 158c is set to μ 1, the coefficientoffrictionμ of the rubbing surface between liner plate 76 and the first friction member 158c is set to μ 6, the coefficientoffrictionμ of the rubbing surface between support plate 160 and the second friction member 162c is set to μ 1, and the coefficientoffrictionμ of the rubbing surface between liner plate 76 and the second friction member 162c is set to μ 7.And, the coefficientoffrictionμ of the rubbing surface between pressing plate 156 and the first friction member 158d is set to μ 1, the coefficientoffrictionμ of the rubbing surface between liner plate 76 and the first friction member 158d is set to μ 8, the coefficientoffrictionμ of the rubbing surface between support plate 160 and the second friction member 162d is set to μ 1, and the coefficientoffrictionμ of the rubbing surface between liner plate 76 and the second friction member 162d is set to μ 9.
At this, above-mentioned each coefficientoffrictionμ 1 ~ μ 9 is set as meeting the relation shown in following formula (7).In other words, the frictional force F1 produced between pressing plate 156 and the first friction member 158a, the frictional force F1 produced between support plate 160 and the second friction member 162a, the frictional force F1 produced between pressing plate 156 and the first friction member 158b, the frictional force F1 produced between support plate 160 and the second friction member 162b, the frictional force F1 produced between pressing plate 156 and the first friction member 158c, the frictional force F1 produced between support plate 160 and the second friction member 162c, the frictional force F1 produced between pressing plate 156 and the first friction member 158d, and the frictional force F1 produced between support plate 160 with the second friction member 162d is equal, and be minimum value.In addition, the frictional force F2 produced between liner plate 76 and the first friction member 158a is greater than frictional force F1.The frictional force F3 produced between liner plate 76 and the second friction member 162a is greater than frictional force F2.The frictional force F4 produced between liner plate 76 and the first friction member 158b is greater than frictional force F3.The frictional force F5 produced between liner plate 76 and the second friction member 162b is greater than frictional force F4.The frictional force F6 produced between liner plate 76 and the first friction member 158c is greater than frictional force F5.The frictional force F7 produced between liner plate 76 and the second friction member 162c is greater than frictional force F6.The frictional force F8 produced between liner plate 76 and the first friction member 158d is greater than frictional force F7.The frictional force F9 produced between liner plate 76 and the second friction member 162d is greater than frictional force F8.Above-mentioned relation is represented with following formula (8).
μ9＞μ8＞μ7＞μ6＞μ5＞μ4＞μ3＞μ2＞μ1···（7）
F9＞F8＞F7＞F6＞F5＞F4＞F3＞F2＞F1···（8）
Based on above-mentioned formula (7) and formula (6), there is the friction member of the large rubbing surface of coefficientoffrictionμ set by between liner plate 76, set larger by the slippage of each first stop member 176 and each second stop member 182 defined.
The action of the torque-limiting mechanism 152 formed as described so is described.Figure 11 represents the torque of damping device 150 and the relation of torsion angle that are delivered to the present embodiment.When torque T is input to damping device 150, torsion angle and torque T increase pro rata.Further, when torsion angle reaches θ 1, be that (rubbing surface between pressing plate 156 and each first friction member 158a ~ 158d, rubbing surface between support plate 160 and second friction member 162a ~ 162d produce and slide for the rubbing surface of μ 1 at coefficientoffrictionμ.Now, sluggish torque T1(=r1 × μ 1 × W is produced).
When torsion angle reaches θ 2, at the first stop member 176a, projection 178 abuts with backstop hole 180a, and the slip between pressing plate 156 and the first friction member 158a is restricted.Then, be produce between the liner plate 76 of μ 2 and the first friction member 158a to slide at coefficientoffrictionμ.In addition, except the rubbing surface except being limited by the first stop member 176a, that coefficientoffrictionμ is μ 1 rubbing surface, then continues to slide.Now, during before torsion angle reaches θ 3, produce sluggish torque T2(=r1 × μ 2 × W).
When torsion angle reaches θ 3, at the second stop member 182a, projection 184 abuts with backstop hole 186a, and the slip between support plate 160 and the second friction member 162a is restricted.Then, be that rubbing surface between the liner plate 76 of μ 3 and the second friction member 162a produces and slides at coefficientoffrictionμ.In addition, except the rubbing surface except being limited by the first stop member 176a, the second stop member 182a, that coefficientoffrictionμ is μ 1 rubbing surface and coefficientoffrictionμ are the rubbing surface of μ 2, slide and also continue.Now, during before torsion angle reaches θ 4, produce sluggish torque T3(=r1 × μ 3 × W).
When torsion angle reaches θ 4, at the first stop member 176b, projection 178 abuts with backstop hole 180b, and the slip between pressing plate 156 and the first friction member 158b is restricted.Then, be produce between the liner plate 76 of μ 4 and the first friction member 158b to slide at coefficientoffrictionμ.In addition, except the rubbing surface except being limited by first stop member 176a, 176b and the second stop member 182a, that coefficientoffrictionμ is μ 1 rubbing surface and coefficientoffrictionμ are the rubbing surface of coefficientoffrictionμ 2, μ 3, slide and also continue.Now, during before torsion angle reaches θ 5, produce sluggish torque T4(r1 × μ 4 × W).
When torsion angle reaches θ 5, at the second stop member 182b, projection 184 abuts with backstop hole 186b, and the slip of support plate 160 and the second friction member 162b is restricted.Then, be produce between the liner plate 76 of μ 5 and the second friction member 162b to slide at coefficientoffrictionμ.In addition, except the rubbing surface except being limited by first stop member 176a, b and second stop member 182a, b, that coefficientoffrictionμ is μ 1 rubbing surface and coefficientoffrictionμ are the rubbing surface of μ 2 ~ μ 4, slide and also continue.Now, during before torsion angle reaches θ 6, produce sluggish torque T5(=r1 × μ 5 × W).
When torsion angle reaches θ 6, at the first stop member 176c, projection 178 abuts with backstop hole 180c, and the slip between pressing plate 156 and the first friction member 158c is restricted.Then, be produce between the liner plate 76 of μ 6 and the first friction member 158c to slide at coefficientoffrictionμ.In addition, except the rubbing surface except being limited by first stop member 176a ~ 176c, second stop member 182a, b, that coefficientoffrictionμ is μ 1 rubbing surface and coefficientoffrictionμ are the rubbing surface of μ 2 ~ μ 5, slide and also continue.Now, during before torsion angle reaches θ 7, produce sluggish torque T6(=r1 × μ 6 × W).
When torsion angle reaches θ 7, at the second stop member 182c, projection 184 abuts with backstop hole 186c, and the slip between support plate 160 and the second friction member 162c is restricted.Then, be produce between the liner plate 76 of μ 7 and the second friction member 162c to slide at coefficientoffrictionμ.In addition, except the rubbing surface except being limited by first stop member 176a ~ 176c, second stop member 182a ~ 182c, that coefficientoffrictionμ is μ 1 rubbing surface and coefficientoffrictionμ are the rubbing surface of μ 2 ~ μ 6, slide and also continue.Now, during before torsion angle reaches θ 8, produce sluggish torque T7(=r1 × μ 7 × W).
When torsion angle reaches θ 8, at the first stop member 176d, projection 178 abuts with backstop hole 180d, and the slip between pressing plate 156 and the first friction member 158d is restricted.Then, be produce between the liner plate 76 of μ 8 and the first friction member 158d to slide at coefficientoffrictionμ.In addition, except the rubbing surface except being limited by first stop member 176a ~ 176d, second stop member 182a ~ 182c, that coefficientoffrictionμ is μ 1 rubbing surface and coefficientoffrictionμ are the rubbing surface of μ 2 ~ μ 7, slide and also continue.Now, during before torsion angle reaches θ 9, produce sluggish torque T8(=r1 × μ 8 × W).
When torsion angle reaches θ 9, at the second stop member 182d, projection 184 abuts with backstop hole 186d, and the slip between support plate 160 and the second friction member 162d is restricted.Then, be produce between the liner plate 76 of μ 9 and the second friction member 162d to slide at coefficientoffrictionμ.In addition, be the rubbing surface of μ 2 ~ μ 8 at coefficientoffrictionμ, slide and also continue.Now, produce sluggish torque T9(=r1 × μ 9 × W), this torque T9 becomes the torque-limiting Tlm of the present embodiment.
So, by circumferentially configuring multiple first friction member 158 and second friction member 162(158a ~ 158d, 162a ~ 162d), thus sluggish torque T1 ~ T8 can be obtained in multistage ground.
As mentioned above, according to the present embodiment, by making multiple first friction member 158a ~ 158d and multiple second friction member 162a ~ 162d different respectively from the coefficientoffrictionμ 1 ~ μ 9 of the rubbing surface of liner plate 76, thus the torque-limiting mechanism 152 obtaining the sluggish torque of multistage by simple structure can be realized.
Embodiment 4
Figure 12 to Figure 14 represents the projection of stop member 90, first stop member 116,176, second stop member 122,182 and other modes in backstop hole that form above-mentioned each embodiment.The stop member 200 of Figure 12 is made up of with the backstop hole 208 of the bottomed cylindrical being formed at friction member 206 the columned projection 204 being such as formed at pressing plate 202.In addition, the wall in backstop hole 208 imbeds the stiffener 210 be made up of the metal of bottomed cylindrical in the mode chimeric with it.Thus, projection 204 abuts with stiffener 210, and does not directly abut with the friction member resin forming friction member 206.Thus, can prevent from reducing because projection 204 and friction member resin directly abut caused durability, damaged.In addition, the shape of stiffener 210 suitably can be changed according to the shape in backstop hole 208.
The stop member 220 of Figure 13 is made up of with the backstop hole 228 of the cylindrical shape being formed at friction member 226 the columned projection 224 being formed at pressing plate 222.In addition, the friction member 226 of the present embodiment is the structure being pasted with the first friction member 232 and the second friction member 234 at the sheet metal 230 of arc-shaped.Further, the peripheral end portion of sheet metal 230 is projected in backstop hole 228.If form stop member 220 like this, then projection 224 abuts with the peripheral end portion of sheet metal 230, does not abut with friction member resin.Thus, can prevent from reducing because projection 224 and friction member resin directly abut caused durability, damaged.
The stop member 240 of Figure 14 is made up of with the backstop hole 250 of the cylindrical shape being formed at friction member 248 the columned projection 246 being formed at pressing plate 242.In addition, cylindric rubber component 252 is embedded with at the outer circumferential face of projection 246.Form stop member 240 if so, then projection 246 does not directly contact with the friction member resin of friction member 248, can relax collision during contact.In addition, as shown in figure 15, when torsion angle 2 lower process 246 contacts with rubber component 252, due to rubber component 252, twisting characteristic changes, and the change from sluggish torque T1 to torque-limiting T2 slowly changes along with the increase of torsion angle.That is, can prevent the switching from sluggish torque T1 to torque-limiting T2 from sharply changing.In addition, the shape of rubber component 252 suitably can change according to the shape of projection 246.
In addition, in fig. 14, projection 246 embeds cylindric rubber component 252, but also can insert spring component between projection 246 and friction member 248.If this spring component is located at the two ends of circumference, then can increase the function making retarding mechanism self-centering.
Above, based on accompanying drawing, embodiments of the invention have been described in detail, but the present invention is also applicable to other modes.
Such as, in the above-described embodiments, projection is cylindrical shape, but may not be defined in this shape, such as, can be square etc.In addition, for backstop hole, also freely can change corresponding to the shape of teat.That is, as long as the structure of the slip of stop member regulation circumference, the shape in teat, backstop hole can freely change.
In addition, in torque-limiting mechanism 152, achieve 8 grades of sluggish torques, but by changing the quantity of the friction member etc. in circumference configuration, can freely change.
In addition, in the above-described embodiments, be provided with retarding mechanism 64 at damping device, but due to sluggish torque can be produced at torque-limiting mechanism 68, therefore can omit this retarding mechanism.
In addition, in the above-described embodiments, at torque-limiting mechanism 152, employ multiple first friction member 158 and multiple second friction member 162, but can be the structure that the first stop member 176 is only set at the first friction member 158, or the structure of the second stop member 182 is only set at the second friction member 162.
In addition, in the above-described embodiments, the first friction member and the second friction member position of inserting can left and right contrary.
In addition, foregoing is only a mode of execution, and the present invention can adopt and carry out various change to the present invention based on the knowledge of those skilled in the art, add and implement in an improved way.
The explanation of reference character
68,102,152: torque-limiting mechanism (vehicle torque restricting means)
76: liner plate
78b, 104b: the second support plate (the second cover plate)
80,106,156: pressing plate (cover plate, the first cover plate)
82,108: belleville spring (pressing member)
88: the first friction members (friction member)
90,200,220,240: stop member
110,158: the first friction members (the first friction member)
112,162: the second friction members (the second friction member)
116,176: the first stop members (the first stop member)
122,182: the second stop members (the second stop member)
160: support plate (the second cover plate)
164: clamp component (pressing member)

Claims (5)

1. a vehicle is with torque restricting means (68,102,152), comprising: the cover plate (80) that can rotate around axle center (C); Can with this cover plate around same axle center the relative liner plate (76) rotated; Be inserted in the friction member (88) between this cover plate and this liner plate; And the pressing member (82,108,164) for producing pressing force between this cover plate and this liner plate, it is characterized in that,
Described cover plate and described friction member are configured to mutually to slide,
Described liner plate and described friction member are configured to mutually to slide,
The frictional force (F2) that the frictional force (F1) that rubbing surface between described cover plate and described friction member produces produces than the rubbing surface between described liner plate and described friction member is little,
The stop member (90) of the slippage specified between this cover plate and this friction member is provided with between described cover plate and described friction member,
When slippage between described cover plate and described friction member becomes specified value, stop the slip between described cover plate and described friction member by described stop member.
2. vehicle torque restricting means according to claim 1 (102,152), is characterized in that,
Described cover plate comprises a pair first cover plates (106,156) and the second cover plate (104b, 160),
As described friction member, between described first cover plate and described liner plate, be inserted with the first friction member (110,158), between described second cover plate and this liner plate, be inserted with the second friction member (112,162),
As described stop member, between described first cover plate and described first friction member, be provided with the first stop member (116,176), between described second cover plate and described second friction member, be provided with the second stop member (122,182),
The slippage that described first stop member specifies is less than the slippage that described second stop member specifies,
The frictional force (F1) that rubbing surface between described first cover plate and described first friction member produces and the frictional force (F1) that the rubbing surface between described second cover plate and described second friction member produces, be less than the frictional force (F2) that the rubbing surface between described liner plate and described first friction member produces
The frictional force that rubbing surface between described liner plate and described first friction member produces is less than the frictional force (F3) that the rubbing surface between this liner plate and described second friction member produces.
3. a vehicle is with torque restricting means (68,102,152), comprising: the cover plate (80) that can rotate around axle center (C); Can with this cover plate around same axle center the relative liner plate (76) rotated; Be inserted in the friction member (88) between this cover plate and this liner plate; And the pressing member (82,108,164) for producing pressing force between this cover plate and this liner plate, it is characterized in that,
Described cover plate and described friction member are configured to mutually to slide,
Described liner plate and described friction member are configured to mutually to slide,
Be configured to: when torque is input to described vehicle torque restricting means, the rubbing surface between described cover plate and described friction member first slides than the rubbing surface between described liner plate and described friction member,
The stop member (90) of the slippage specified between this cover plate and this friction member is provided with between described cover plate and described friction member,
When slippage between described cover plate and described friction member becomes specified value, stop the slip between described cover plate and described friction member by described stop member.
4. vehicle torque restricting means (102) according to claim 3, is characterized in that,
Described cover plate comprises a pair first cover plates (106) and the second cover plate (104b),
As described friction member, between described first cover plate and described liner plate, be inserted with the first friction member (110), between described second cover plate and this liner plate, be inserted with the second friction member (112),
As described stop member, between described first cover plate and described first friction member, be provided with the first stop member (116), between described second cover plate and described second friction member, be provided with the second stop member (122),
The slippage that described first stop member specifies is less than the slippage that described second stop member specifies,
When torque is input to described vehicle torque restricting means, rubbing surface between described first cover plate and described first friction member and the rubbing surface between described second cover plate and described second friction member slide at first, then, rubbing surface between described liner plate and described first friction member slides, finally, the rubbing surface between this liner plate and described second friction member slides.
5. the vehicle according to claim 2 or 4, with torque restricting means (152), is characterized in that,
Described vehicle torque restricting means comprises:
First friction member (158) described in the multi-disc of configured separate in the circumferential;
Multiple described first stop member (176) of the slippage of regulation this first friction member of multi-disc and described first cover plate (156);
Second friction member (162) described in the multi-disc of configured separate in the circumferential; With
Multiple described second stop member (182) of the slippage of regulation this second friction member of multi-disc and described second cover plate (160),
Described multi-disc first friction member and multi-disc second friction member have mutually different friction factor (μ) between described liner plate,
Have the friction member of the large rubbing surface of friction factor between described liner plate, the slippage of described first stop member or described second stop member defined is set larger.
CN201180071488.1A 2011-06-06 2011-06-06 Vehicle torque restricting means Expired - Fee Related CN103597230B (en)

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Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103899668B (en) * 2012-12-28 2018-02-06 华域三电汽车空调有限公司 compressor and torque limiter
DE102017120530A1 (en) * 2017-09-06 2019-03-07 Schaeffler Technologies AG & Co. KG Slip clutch with a rotation axis
DE102017121437A1 (en) * 2017-09-15 2019-03-21 Schaeffler Technologies AG & Co. KG Torque limiter for a drive train
DE102017121431A1 (en) * 2017-09-15 2019-03-21 Schaeffler Technologies AG & Co. KG Torque limiter for a drive train
JP6666605B2 (en) * 2018-08-01 2020-03-18 株式会社エフ・シー・シー Torque damper device
DE102019100372A1 (en) * 2019-01-09 2020-07-09 Schaeffler Technologies AG & Co. KG Clutch disc with a damper unit for a friction clutch
JP7267046B2 (en) * 2019-03-15 2023-05-01 株式会社エクセディ damper device
JP7340403B2 (en) * 2019-10-02 2023-09-07 株式会社エクセディ Torque limiter and power transmission device
JP7417397B2 (en) * 2019-10-02 2024-01-18 株式会社エクセディ Torque limiter and power transmission device
JP2022035363A (en) * 2020-08-20 2022-03-04 株式会社エクセディ Damper device
CN112855798B (en) * 2021-03-03 2023-01-03 舍弗勒技术股份两合公司 Torque limiting device, torque transmission device, and vehicle
DE102022126302B3 (en) 2022-10-11 2024-01-25 Schaeffler Technologies AG & Co. KG Torque limiting device

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5120276A (en) * 1984-06-12 1992-06-09 Luk Lamellen Und Kupplungsbau Gmbh Torsion damping apparatus for use with friction clutches in the power trains of motor vehicles
CN2828429Y (en) * 2003-10-31 2006-10-18 爱信精机株式会社 Ripple torque absoption device

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3775998A (en) * 1972-04-14 1973-12-04 Allied Steel Tractor Prod Inc Safety clutch
US5154683A (en) * 1991-11-19 1992-10-13 Dana Corporation Clutch having rotatable friction rings
JP4581576B2 (en) 2003-09-29 2010-11-17 アイシン精機株式会社 Torque fluctuation absorber
JP4725348B2 (en) * 2006-02-16 2011-07-13 アイシン精機株式会社 Torque fluctuation absorber
JP4747875B2 (en) 2006-02-16 2011-08-17 アイシン精機株式会社 Torque fluctuation absorber
JP4882642B2 (en) * 2006-09-29 2012-02-22 アイシン精機株式会社 Torque fluctuation absorber
JP4894467B2 (en) * 2006-11-08 2012-03-14 アイシン精機株式会社 Torque fluctuation absorber
JP4941115B2 (en) * 2007-06-08 2012-05-30 アイシン精機株式会社 Torque fluctuation absorber
JP5604906B2 (en) 2009-03-05 2014-10-15 アイシン精機株式会社 Torque fluctuation absorber
JP2010223294A (en) * 2009-03-23 2010-10-07 Aisin Chem Co Ltd Dry-type frictional material
JP5481897B2 (en) 2009-03-25 2014-04-23 アイシン精機株式会社 Torque fluctuation absorber
JP5244673B2 (en) * 2009-03-31 2013-07-24 トヨタ自動車株式会社 Torque limiter mechanism
JP5691367B2 (en) * 2009-10-27 2015-04-01 アイシン精機株式会社 Torque fluctuation absorber
JP2012102755A (en) * 2010-11-05 2012-05-31 Aisin Chemical Co Ltd Torque limiter for vehicle
JP2016070323A (en) * 2014-09-29 2016-05-09 アイシン精機株式会社 Friction buffer device

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5120276A (en) * 1984-06-12 1992-06-09 Luk Lamellen Und Kupplungsbau Gmbh Torsion damping apparatus for use with friction clutches in the power trains of motor vehicles
CN2828429Y (en) * 2003-10-31 2006-10-18 爱信精机株式会社 Ripple torque absoption device

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